Control system for refuse handling apparatus

ABSTRACT

A refuse truck of the rear loading type provided with a novel packer blade and associated control apparatus. More specifically, this invention relates to a novel control means for the above apparatus that eliminates complex valving.

United States Patent [191 Clucker Nov. 13, 1973 Meter 60/52 S Jackson 60/52 S [5 CONTROL SYSTEM FOR REFUSE 2,603,065 7/1 952 Sarto HANDLING APPARATUS 3,667,629 6/1972 2,799,996 7/1957 [76] Inventor: Richard V. Clucker, 633 N. Cherry 2 302 74 3 957 St., Kenton, Ohio Oct. 7, 1971 Primary Examiner-Albert J. Makay Att0rneySchmieding and Fultz [22] Filed:

Appl. No.: 187,337

[57] ABSTRACT A refuse truck of the rear loading type provided with a novel packer blade and associated control apparatus. More specifically, this invention relates to a novel [52] US. 214/833, 60/52 S [51] Int. B65f 3/00 [58] Field of Search..................... 214/833, 503, 82;

control means for the above apparatus that eliminates complex valving.

[56] References Cited UNITED STATES. PATENTS 2 Claims, 18 Drawing Figures 3,476,273 11/1969 Jones et 214/82 Pmmmmv 13' Ian SHEET 010F 13 g jufliz ATT NEYS PAIENIEDnnv 13 ms MEI; 020$ 13 Pig. 2.

- INVENTOR. R/CHA RD 1/. CL UCKER g $111. ATTo NEvs PMFNIEUNHY 131m;

SHKEI 030F 13 INVENTOR.

RICHARD M CLUCKER .Pmmmuuv 13 ms 3.771.674

SNKEI Uh 0F 13 52 POS/T/ON 2.

Pig. 4.

INVENTOR. RICHARD ll CLUCKER TTOENEYS PAIENIEUnuv 13 '91s SHEEI 05 0F 13 INVENTOR. RICHARD VCLUCKER ATTO Y5 m ZOPQWOQ SHEET UB0? 13 PATENTEUNUY 13 ms INVENTOR.

ATTO EYS SHEET 07H? 13 F 8. I INVENTOR.

RICHARD M CL UCKER ATT RNEYS PATENTEI] NEW 13 I975 saw 080! 13 INVENTOR. RICHARD V CLUCKER BY 14%; \Z-lt z ATTO EYS l4 q L PATENTEDnnv 13 1915 3371, 57

sum 090E 13 INVENTOR. RICHARD 1/. CLUCKER J lia ATT NEVS P I NIEnuuv 13 ms 3771.674

sum 13m 13 Fag. 12 Z6 42/ INVENTOR. RICHARD M CLUCKER ATT NEVS CONTROL SYSTEM FOR REFUSE HANDLING APPARATUS a carriage that is arranged to reciprocate on an inclined track means so as to load and pack the forward body portion.

In refuse collecting vehicles of this type a problem has been present in that operators, in the interest of expediting matters, tend to overload the driving means of I the packer blade mechanism and its control system, by running the vehicle engine at excessive speed with the result that excessive volumetric flows of hydraulic fluid are delivered to the packer blade control mechanism.

In accordance with the present invention, the present packer blade driving and control. mechanism is provided with means for establishing a maximum predeter? mined volumetric flow of fluid delivered to the hydraulic control system for the packer blade independently of any increases. in the speed of the vehicle engine which may be established by the operator.

Another problem with refuse vehicle of the type described has resulted from the misuse of the automatic throttle control means or governor which is commonly present on vehicles of this type for automatically stepping up engine RPM to provide'additional energy for the load created on the packer blade hydraulic system during a packing operation. v

In accordance with the present invention a novel limiting means is provided for preventing operation of said automatic throttle control means as a function of the manual transmission control lever.

It is a primary object of thepresent invention to provide a refuse truck of the type described which includes a unique hydraulic system for activating the packer blade that includes a fluid motor and pump arrangement in combination with flow control means associated with the fluid circuit for delivering a predetermined volumetric flow of fluid to the fluid motor with the volumetric flow being independent of increases in the speed of the vehicle engine.

It is another object of the present invention to provide a refuse truck of the type described which includes a novel means for preventing operation of an automatic throttle control means when the gear shift control for the vehicle transmission is shifted from a neutral position wherein packing is normally accomplished and a drive position wherein the vehicle is progressing along the road. 1

Another aspect of the present invention is to provide a refuse truck of the type described that includes a plurality of pressure responsive controllers that respectively control a plurality of cycles, each being arranged to be preset by a common manual actuator, so as to be subsequently pressure triggered sequentially by predetermined system pressure values. Moreover, the plurality of pressure responsive controllers can also be manually uncocked by said common manual controller thereby terminating operation of the packer blade 2 mechanism and its carriage at any position in their paths of movement.

As another aspect of the present invention, after the packer blade mechanism has been stopped at some position as described above, the common manual actuator can be used to reset the plurality of pressure actuated controllers which will then restart operation of the packer blade mechanism and said controllers will function to cause the packer blade to automatically return to and complete certain of said cycles in predetermined priority and sequence.

As still another aspect of the present invention, when the packer blade is being moved through one of the above mentioned cycles wherein it is caused to first engage the refuse and in the event it engages a foreign object that becomes jammed between said blade and the bottom wall of the loading opening, then in'that event the respective pressure responsive controller for such cycle will automatically arrest the blade actuating cylinder responsive to a predetermined system pressure value thereby releasing the fluid pressureon'the packing blade. At the same time, the next successive or blade retraction cycle will automatically be negotiated whereby the packing blade is dragged freely past said foreign object.

As another aspect of the present invention, in addition to the above described automatic cycling operation the novel control system is also adapted for what may be termed jog type operation whereby the operator can individually actuate a manual control lever that energized only the hydraulic cylinder for reciprocating the carriage in its track or a second manual control lever that energizes only the hydraulic cylinder for pivoting the packing blade. Moreover, the operator can actuate these levers to accomplish either short or long paths of movement of the carriage or blade as may be desired. As an advantageous result the operator has the ability to stop the machine during automatic cycling. and then use such jog type'control to move the packing blade away from a clogging object, or perhaps stop the packing blade and move it away from an object that he does not desire to pack.

As another aspect of the present invention the present novel control system has a decided advantage in that it is adapted to proceed from an interrupted cycle of movement to thenext successive cycle of the packing blade withoutthe necessity of reversing the mechanism back to its prior path of movement. As a result the movement of the mechanism and force being applied by the packing blade to the load can be terminated and the carriage can be moved to drag the arrested packing blade past the refuse.

As still another aspect of the present invention, the novel control system is so arranged that if movement of the packing blade is manually stopped during a refuse engaging cycle, and then restarted by the operator, the packing blade will always raise away from engagement with an obstructing object, let such object re-position itself, after which the blade will automatically take a new pressurized engagementwith such re-positioned object.

It is still another aspect of the present invention to provide a novel control apparatus of relatively simple design requiring only a minimum of adjustments. More specifically, the only adjustment required is the setting of a single pressure setting screw in each of a plurality of pressure responsive controllers so as to preselect the above described predetermined pressure at which each controller is actuated.

As still another aspect of the present invention, the novel control system, being pressure responsive, eliminates the need for limit switches and mechanical linkages to actuate control valves. Such elements have been sources of mechanical trouble in prior devices in that they have the tendency to become worn and distorted whereby the accuracy of control is lost.

Further objects and advantages of the present invention will be apparent from the following description, reference being had to the accompanying drawings wherein a preferred form of embodiment of the invention is clearly shown.

IN THE DRAWINGS FIG. 1 is a partial rear perspective view illustrating a rear loader type refuse truck to which the apparatus of the present invention has been applied;

FIG. 2 is a partial rear view, in broken section, showing the packer blade and carriage apparatus comprising a portion of the present invention;

FIGS. 3 through 6 are side sectional views of a rear body portion and apparatus of FIG. 2, the section being taken along a vertical plane through the centerline of such body portion;

FIG. 7 is a top elevational view, partially in section, of a pressure responsive control means comprising a portion of the apparatus of the present invention, the section being taken along a horizontal plane through the centerline of such control means;

FIG. 8 is an end sectional view of the pressure responsive control means of FIG. 7;

FIG. 9 is a partial top sectional view of the control means of the preceding figures, the section being taken along a horizontal plane through such control means;

FIG. 9-A is a sectional view showing the interior of a pressure responsive controller comprising a portion of the control means of the preceding figures, the section being taken along a plane through the centerline of such controller;

FIG. 10 is a side elevational view of a manual actuator mechanism comprising a portion of the apparatus of the present invention;

FIG. 11 is a side elevational view of the mechanism of FIG. 10;

FIGS. 12 through 16 are diagrammatic views illustrating various flow cycles through a hydraulic circuit comprising a portion of the apparatus of the present invention; and

FIG. 17 is a sectional view of a flow divider mechanism comprising a portion of the control system of FIGS. 12 through 16, said section being taken along a vertical plane through the centerline of the flow divider mechanism.

Referring in detail to the drawings, FIGS. 1 and 2 illustrate a rear loader type refuse truck that includes a forward refuse receiving body portion indicated generally at 20 and a rear packer body portion indicated generally at 22. Rear body portion 22 is pivotally attached to the forward body portion 20 at a pivot 48, FIG. 4, and a hydraulic cylinder 21 is operatively connected between the forward and rear body portions at the pivots 23 and 25. Rear body portion 22 can be pivoted upwardly and away from front body portion 20 by extension of hydraulic cylinder 21 thereby permitting unloading of front body portion 20 after it has been packed with refuse.

With continued reference to FIG. 1, forward body portion 20 includes side walls 24, a top wall 26, a bottom wall 28 and a front wall 29 which define a refuse receptacle into which the packing apparatus on the rear body portion 22 functions to load and pack refuse.

Referring next to FIGS. 2 6, rear body portion 22 includes a carriage indicated generally at 68 which is mounted for reciprocation on inclined tracks 62 sup ported by side walls 30 of rear body portion 22.

Carriage 68 includes an upper shaft 60, the ends of which are provided with rollers 66 that run in track 62 and a lower shaft 58, the ends of which are provided with similar rollers 66 which also are mounted in the track.

Carriage 68 further includes outwardly extending brackets 46 which are pivotally attached to a pair of carriage actuating hydraulic cylinders 40 at the pivot pins 47. The lower end of hydraulic cylinders 40 at the pivot pins 47. The lower end of hydraulic cylinders 40 are similarly pivotally attached to the side wall .30 of the rear body portion by the pivot pins 41 in brackets 44. It will now be understood that when carriage actuating cylinders 40 are pressurized in their upper chambers then cylinder rods 42 and carriage 68 are retracted downwardly and, conversely, when the other ends of the cylinders 40 are pressurized the cylinder rods and carriage will be extended upwardly.

With reference to FIGS. 2 through 6, a packing blade includes collars 64 which are pivotally mounted on shaft 58 and a blade actuating cylinder 52 includes an inner end pivotally mounted on carriage 68 at upper shaft and an extendable ram 54, the outer end of which is pivotally connected to packer blade 50 at a pivotal connection 56. It will now be understood that when blade actuating cylinder 52 is pressurized so as to extend ram 54 the packing blade will be pivotted about lower shaft 58 from Position 2 to Position 3. Conversely when the other side of cylinder 52 is pressurized, so as to withdraw ram 54, then packer blade 50 will be raised from Position 3 to Position 2.

It should be mentioned that the operators load refuse into the rear body portion 22 via a rear opening 34 such that the refuse is disposed on a bottom wall 36.

In general,-when packing blade 50, just described, moves from Position 2 to Position 3 blade 50 will engage the refuse and, during a subsequent cycle, later to be described, when carriage actuating cylinder 40 is extended to raise carriage 68 from Position 3 to Position 4 then the refuse is further moved up into the previously described receptacle formed by forward body portion 20. As the forward body portion becomes filled the carriage actuating cylinders 40 serve to compress and pack the load.

Reference is next made to the novel control means of the present invention illustrated in FIGS. 7 through 16 which, in general, functionsto automatically cycle the above mentioned carriage 68 and packing blade 50 through four pressure responsive cycles, when automatic actuation of the packer blade is desired. It should further be stated the control system is further adapted to permit selective independent jog actuation of either the packer blade alone or the carriage alone by the selective actuation of individual manual control levers which can be utilized by the operator when desired as will later be described in detail.

CYCLE 2- Carriage 68 moves from Position 1 to Po-' sition 2 CYCLE 3 Packer blade 50 moves from Position 2 to Position 3 CYCLE 4 Carriage 68 moves from Position 3 to P0- sition 4 It should further be generally mentioned that FIG. 12

illustrates the hydraulic circuit for the control system when the mechanism is in Neutral.

FIG. 13 illustrates the hydraulic circuit for the control system during cycle 1.

FIG. 14 illustrates the hydraulic circuit for the control system during cycle 2. I

FIG. 15 illustrates the hydraulic circuit for the con-- trol system during cycle 3.

FIG. 16 illustrates the hydraulic circuit for the control system during cycle 4.

Reference is next made to FIGS. 2, 7, and 8 which illustrate a pressure responsive control means indicated generally at 71). Such control means 70 is mounted on the frame of rear body portion beneath the cover 32, and is actuated by a manual control mechanism 120 mounted on right side wall 30 of rear body portion 22, said mechanism being shown in enlarged detail in FIGS. and 11.

As seen in FIG. 10 and FIG. 11, a master manual actuator is indicated generally at 120 and includes a handle portion 126 that is pivotally mounted to the rear body portion on a pivot rod 135. Handle 126 includes a common bar 137 provided with four adjusting screws 139 each of which engages a lower arm of a respective bell crank lever 121 through 124. When master actuator handle 126 is pushed inwardly toward the body, FIG. 11, the inner ends of adjusting screws'139 depress the lower arms of bell crank levers 121 through 124 causing them to pivot about pivot shaft 135 and thereby extend push rods 128, 130, 132 and 134 upwardly. Such upward movement of the push rods actuate the respective upper bell crank levers 136 142 which move four horizontal actuating rods 141, 143, 145 and 147 inwardly toward the rear body portion. Each of these rods includes a pivotal connection with a respective one of the spools 1 4 of the control means "70 of FIGS. 7 through 9 A. Hence, it will be understood that when master manual controller 120 is pushed inwardly, for automatic operation, all four spools 1 4 are shifted from a centered position to a right position as viewed in FIG. 9 and when such master controller is pulled out spools 1 4 return to the centered position of FIG. 9.

At this time it should be mentioned that two of the lower bell crank levers 122 and 123, FIGS. 10 and 11, have extended lower arms which form individual manual actuators for each of the two center spools 2 and 3 of the control means 70 of FIGS. 7 through 9-A. Lever 122 can be individually actuated to perform a manual jog operation of carriage 48 and that when this lever is pushed inwardly toward the rear body portion spool 2 is actuated from a centered position to the right, FIG. 9, and when individual lever 122 is pulled outwardly from the rear body portion then such spool 2 is actuated outwardly to the left.

Similarly when the other lever 123 is pushed inwardly then only spool 3 is shifted from a centered position to the right, FIG. 9, and when such individual actuator 123 is pulled outwardly then spool 3 is shifted from the centered position to the left.

The jog type operation which results from such individual actuation of spools 2 and 3 will be explained in detail later herein.

Reference is next made to FIGS. 7 through 9-A which illustrate a pressure responsive control means indicated generally at which includes an outer housing portion 322 and an inner housing portion 324 separated by a drain passage 2110 that communicates with an outlet passage 78 leading back to reservoir 101, FIGS. 12 16. As previously mentioned the four spools 1 through 4 can be shifted from the centered positions illustrated to right or actuated positions by master manual actuator handle 126 just described.

As seen in FIG. 7, four separate pressure responsive controllers are indicated generally at 71 through 74, one for each of the spools 1 4. The interior of one of such controllers 71 74 is illustrated in enlarged detail in FIG. 9-A and the operation of this device will be described in detail later herein.

AUTOMATIC OPERATION OF THE CONTROL SYSTEM Neutral As seen in the flow diagrams of FIGS. 12 16 a pump 81 driven by the vehicle engine provides pressurized fluid for the system. When the previously described master actuator handle 126 is in its neutral position all of the spools 1- 4 are centered, FIG. 9, whereby the central grooves in the spools form an open passage through control means 70 as is indicated schematically in dotted delineation at 109 in FIG. 12. Such schematically represented passage 109 is formed by the individual passages in valve body 324 as seen in detail in FIG. 9 at 76, 228, 254, 282 and 78.

Cycle 1 1 When the master actuator handle 126, FIGS. 10 and 11, is pressed .inwardly toward the body all four spools 1 4 are shifted from centered positions C to right or actuated positions R as seen in FIG. 9 wherein the spools are releasably retained in such actuated positions by the pressure responsive controllers 71 74. As

seen in FIG. 9-A, the spools are thus retained since sleeve portions 320 on the right ends of the spools shift the balls 326 into respective detents 328 formed in the controller housings 3211.

During cycle I packer blade 50 is moved from the position of FIG. 4 to the position of FIG. 1 and only the blade actuating cylinder '52 is pressurized in a direction to retract the ram 54 of such cylinder.

As seen inFIGQ9, with all four spools retained in actuated positions R spool 1 is first in line to receive the pressurized flow from inlet 76 and the flow will be released through a first pressurized outlet port 80, FIGS. 7 and 13, and then via line 87 to the retraction chamber of blade actuating cylinder 52. As seen in FIG. 9 the above described circuit connection is made within control means 70 via passage 76, passage 212 and recess 216 in spool 1 which connects annular housing recesses 204 andl206 when spool 1 is shifted to the right position. It should be mentioned that the left housing recess 204 communicates with the previously mentiond outlet port 80 which in turn communicates with the retraction chamber of blade actuating cylinder 52.

With continued reference to FIG. 9 when spool l is in its right position housing recess 224 is connected to drain passage 200 via spool recess 222. This serves to connect port 82 in the control means housing, FIG. 7 with line 89 in the circuit of FIG. 13 that drains the ex tension chamber of blade actuating cylinder 52 to tank 181 via line 89, drain passage 200 through the valve housing and line 85 back to tank 101.

As seen in FIGS. 9 and 9-A, with spool 1 is shifted. to the right, in its actuated position, an axial detector passage 218 and radial detector passage 214 receive pressurized oil from housing passage 76 and thereby transmit system pressure to a poppet 226 of pressure responsive controller 71. When the pressure reaches some predetermined value, for example 1,300 psi, poppet 226 is unseated thereby shifting a cam surface 330 to the right, FIG. 9-A, whereby a compressed main spring 348 drives spool 1 back to its centered open position thereby opening passage 228 leading to spool 2. It should be pointed out that main spring 348 is operatively compressed between a right spring seat 346 and a left spring seat 352, the latter being in engagement with the right end of spool sleeve 362 as seen in FIG. 9-A.

It shouldbe mentioned that the predetermined pressure referred to above is established by pressure setting screw 344 which is axially movable in a threaded bore 342 in annular member 344 which is in turn mounted in the spool sleeve 362 at a threaded junction 366. Manipulation of pressure setting screw 344 varies the bias on a compression spring 368 interposed between poppet 226 and a rod extension 354 carried bypressure setting screw 344. The inner end of such rod extension 354 includes a fixed spring retainer member 358 and the rod also extends through a guide and spring housing member 356. When pressure setting screw 344 is actuated, spring 368 is compressed or decompressed to pro vide the necessary preloaded force on poppet 226 to provide the previously mentioned predetermined pressure at which the spool is returned from its right to its centered position.

Cycle 2 The function of cycle 2 is to move carrige 48 from Position I to Position 2 by pressurizing only the retraction chamber of carriage actuating cylinder 40.

The circuit flow for cycle 2 is illustrated in FIG. 14 and the internal operation of control means 70 is shown in FIG. 9.

Referring to FIG. 9, after spool 1 has been reset to its centered position, at the predeterminedpressure value arrived at at the end of cycle 1 when the blade actuating cylinder ram is fully retracted, spool 2, still being in its set position to the right, is the next spool to receive pressurized fluid via passages 76 and 228.

Since spool 2 is shifted to the right a second outlet port 84 in the control means housing, FIG. 7, is pressurized via housing chamber 228, passage 230, and annular housing grooves 232 and 236, the latter being connected via spool recess 234.

At the same time a right spool recess 249 connects a second drain port 86 in the control means housing, FIG. 7, with tank via annular housing groove 250 drain passage 200, and outlet port 76 connected to reservoir line 85.

As seen in FIG. 14 in such cycle 2 position pressurized port 84 is connected to the retraction side of carriage actuating cylinder 40 via line 93 and the other side of the carriage actuating cylinder is drained to low pressure port 86 via line 91. This causes rams 42 of the carriage actuating cylinder to retract to the end of its stroke at which time the system pressure builds up to a predetermined pressure value established by the setting of pressure setting screw 344 of pressure responsive controller 72. Such controller then shifts spool 2 back to its neutral open centered position in the manner previously described thereby terminating cycle 2.

Cycle 3 During this cycle packer blade 50 is moved from its raised Position 2 to its lowered Position 3.

With spool 2 reset in its neutral open centered position spool 3 is in turn subjected to pressure via passage 254 and is disposed in its set position. Hence the third pressurized port 88, FIG. 7, is pressurized via housing port 254, passage 256 and annular housing grooves 258 and 260, the latter being connected by spool recess 264. At the same time housing port and right housing groove 280 are connected to tank passage 200 via spool recess 278.

With spool 3 shifted to the right and making the connections just described the flow diagram of cycle 3 is set up as seen in FIG. 15 wherein the third pressurized port 88 delivers pressurized oil to the extension side of blade actuating cylinder 52 via a line 89 and the other side of such cylinder is drained to tank via line 87, drain port 90, drain passage 200 in controllers body and line 85 to tank 101.

It should be mentioned that line 87, FIG. 15, is provided with a pilot operated check valve which is opened by the pressurization of line 89 thereby permitting the drain of the ram side of the blade actuating cylinder 52. r

In the circuit position of cycle 3 after blade 50 is moved from the raised Position 2 of FIG. 4 to the refuse engaging Position 3 of FIG. 5 and the ram 54 of blade actuating cylinder 52 is extended to its limit at which time the pressure rises to a predetermined pressure value, then the next pressure responsive controller 73 functions to release spool 3 back to its centered open position, as previously described and cycle 3 is terminated.

It should be mentioned that when spool 3 was in its actuated position its respective poppet 226 communicates with pressurized fluid via axial detector passage 276, radial detector passage 270, housing recess 272, and passage 256, the latter being connected to pressure via passages 254, 228 and 76.

Cycle 4 housing grooves 288 and 292, the latter being connected by spool recess 290.

At the same time a right housing port 94 and recess 306 are connected with drain passage 200 in the control means housing via spool recess 304.

As seen in FIG. 16, with the above described connections for cycle 4 the fourth pressurized port 92 delivers pressurized oil to the extension side of carriage actuating cylinder 40 via line 91 and line 93 drains the other side of carriage actuating cylinder 40 via pilot operated check valve 99 and line 97, thence into drain port 94 in the valve housing, through drain passage 200 and line 85 to tank 101.

It should next be mentioned that a poppet element 226 of pressure responsive controller 74 communicates with pressurized fluid via detector passages 298 and 302, housing recess 300, and housing passages 284, 282, 254, 223 and 76.

When carriage actuating cylinder 40 reaches the end of its extension stroke, with carriage 66 in Postion 4, then a pressure build-up occurs in the system up to some predetermined pressure value at which time the next pressure responsive controller 74 shifts spool 4 in its centered opened position wherein housing passage 282 communicates with drain port 78 thereby returning the flow to the neutral position of FIG. 12.

It will now be seen that the four cycles of automatic pressure responsive actuation have automatically occurred from a single setting of the master manual actuator 126.

In so doing it will be understood that the packing blade 50 and carriage 48 have been sequentially cycled from Postion 4 through Postions 1, 2 and 3 and then back to Position 4 responsive to the sequentially effective preset pressure signals.

JOG TYPE OPERATION OF THE CONTROL SYSTEM As previously described herein with connection with FIGS. and 11 spool 2 can be individually actuated by individual manual actuator I22 and similarly spool 3 can be individually actuated by individual manual actuator 123.

ln jog operation of carriage 68, manual actuator 122 can either be pressed inwardly toward the body to move spool 2 to the right, FIG. 9, and thereby set up the cycle 2 flow of FIG. 14 required to retract cylinder 40 and move carriage 68 from Position l to Position 2. In addition, individual actuator 122 can be actuated away from the body to shift the spool 2 to the left, FIG. 9, thereby reversing the pressurization of the second housing ports 84 and 86. With spool 2 shifted to the left the cycle 2 flow of FIG. 14 is reversed with line 91 on extension side of cylinder 40 being pressurized via port 85 and line 91 and with the other side of such packing cylinder being drained via line 93 and port 84. In such left spool position for spool 2 the right housing groove 250 is pressurized by spool groove 242 which connects housing recesses 242 and 250 which in turn are pressurized via passage 230, 228 and 76. At the same time housing port 84 is connected to drain passage 200 via housing recess 232 and spool recess 234.

Referring next to jog operation of packing blade 50, the other individual manual actuator 123 can either be pressed inwardly toward the body thereby moving spool 3 to the right which sets up the cycle 3 flow of FIG. 15 wherein only the extension side of blade actuating cylinder 52 is pressurized. When, however, manual actuator 123 is pulled outwardly away from the body the connection to the third housing ports 88 and 90 are reversed with respect to the flow diagram shown in FIG. 15 thereby connecting the retracting side of blade actuating cylinder 52 with pressure whereby the ram 54 is retracted. With spool 3 in the left position, FIG. 9, port 90 is pressurized via housing groove 280 and 272 which are connected by spool groove 278. These are in turn pressurized by passage 256, 254, 228 and 76. At the same time left housing groove 260 is connected to drain passage 200 via spool groove 264.

In such left position of spool 3 it will now be understood that packing blade 50 is raised from the refuse engaging Position 3 to the raised Position 2.

In view of the above, it will now be understood that the operator can easily effect jogging control by either manipulating only individual actuator 122 to move carriage 48 either upwardly or downwardly along its track 62 for either short or long strokes, and by actuating only individual actuator 123 the operator can pivot packing blade 50 between Positions 2 and 3 either with short or long strokes as may be required.

It should further be stated that the primary purpose for the above described jogging capability is to permit the operator to move the packing blade 50 or carriage 48 as may be required to move away from a foreign object that is clogging operation, or to stop the blade or carriage to save an object that the operator does not desire to pack.

In further description of the operation it should be mentioned that the individual pressure responsive controllers 71 74 described above will function sequentially as they are located successively downstream from the pressure source and at any time the high pressure fluid is presented to one of the spools 1 4 while in its actuated position to the right the control system will perform its respective cycle up to the predetermined pressure value for the pressure responsive controller for the particular spool. The system will then proceed to the next succeeding cycle.

As an important advantage of the operation, in the event the mechanism is going through cycle 3 wherein packing blade 50 is being pivotted downwardly from the upper Position 2 toward the lower Position 3, and when the blade engages an object that is too strong to be crushed and packed, such object will arrest downward movement of blade 50, prior to its reaching Position 3, thereby causing a build-up in system pressure which will cause pressure responsive controller '73 to release spool 3 to its centered neutral position. Pressurized oil will next pass on to the next successive spool 4 which is in its cocked position whereby the control system will proceed through cycle 4 and return to neutral.

It should further be mentioned that a foreign object may be engaged when the packing blade has been pivotted from Position 2 to Position 3. The manual actuator can be used to stop the machine, with the packing blade in the obstructed position between Positions 2 and 3. Next the machine can be restarted by actuating manual actuator 126. All four spools will again be cooked. Upon such restarting of the machine, cycle 2 will take priority which causes spool 2 to set up the flow required to raise packer blade $0 and thereby reset it against the load. The control system will then proceed to go through cycles 3 and 4 and return to neutral. This is an advantageous feature since such automatic priority of cycle 2 raises the packing blade thereby permitting the obstructing object to reposiition before the blade automatically returns to engagement with such object.

Assuming that the machine is going through cycle 1 and the machine is stopped and restarted by operating the master actuator 126, all three spools are reset but spool 1, having already completed its function, will automatically be released back to neutral and the control system will then automatically proceed through cycles 2, 3 and 4 and back to neutral. It will be understood that spool 1 had completed its function since ram 54 of blade actuating cylinder 52 had been moved completely to its limit prior to the commencement of cycle 2.

In the event that the control system is negotiating cycle 2 and is for any reason stopped and restarted, packing cylinder 40 will complete its retraction and terminate cycle 2 and the system will then go through cycles 3 and 4 and return to neutral.

In the event the system is negotiating cycle 4 from Position 3 to Position 4 and is stopped and then restarted, spool 2 will take priority. The machine will reset the blade 50, repeat cycle -3, then finish cycle 4 and then return to neutral at which time movement of the blade and carriage are terminated.

Referring again to FIGS. 12 16, the control system is further provided with novel flow control means associated with the hydraulic circuit for delivering a predetermined volumetric flow of fluid from the previously mentioned pump 81 with the maximum volumetric flow being independent of any increases in the speed of the vehicle engine 400. A

As seen in FIGS. 12 16, engine means indicated generally at 400 includes an engine portion 401 that drives a transmission 403 provided with a conventional power take-off 402.

A drive shaft 404 connects power take-off 402 with pump 81 which includes a pump inlet 83 communicating with a fluid reservoir means 101.

Fluid from pump 81 is delivered to a flow divider indicated generally at 420 with said flow divider including a main outlet 421 communicating with the previously described control valve 70 and an auxiliary outlet leading back to reservoir means 101.

A pressure relief valve 419 is provided between flow divider 420 and pmp 81 to establish the overall system pressure.

Flow divider 420 is of the pressure compensated combination bypass and restrictive type which functions to deliver a constant predetermined volumetric flow from pump 81 to valve 70 and any flow generated by pump 81 in excess of said predetermined volumetric flow is bypassed back to tank 101 by action of said flow divider 420.

It should be mentioned that flow divider 420 and fixed displacement pump 81 could be replaced by other maximum flow limiting means, such as a variable volume pump of the type disclosed in U.S. Pat. No. 3,183,847 without departing from the spirit of the present invention.

With reference to FIG. 17, the interior of flow divider 420 is shown and it will be noted that it includes an inlet 436 that communicates with an outlet 421 leading to control valve 70.

Any volumetric flow in excess of a predetermined volume established by adjusting needle valve 440 442 via control knob 422 is bypassed back to tank 101 via outlet 430 upon yielding of piston 428 against the action of control spring 434.

Reference is again made to FIGS. 12 16 which illustrate another aspect of the present invention wherein a limit switch 414 is provided for permitting operation of an automatic throttle control means indicated generally at 417 only when a manual shift of transmission actuator 406 is positioned in a neutral position N by the operators actuation of a gear selector 408.

It should be mentioned that when lever 408 is in the neutral position N, limit switch 414 bridges contacts 410 412 thereby connecting the automatic throttle control means 417 with battery 416. Such closing of limit switch 414 renders automatic throttle control means operative, automatically, such that the normal idle speed of engine 401 is increased, for example from 600 RPM to 900 RPM, so as to speed up pump 81 to the extent that the volumetric fluid delivery therefrom is sufficient to adequately power fluid motors 40 and 52 which in turn actuate the power blade.

I claim:

1. A refuse truck comprising, in combination, a refuse receiving body including a load receiving opening; a packer blade moveably mounted on said body and including a compacting surface for engaging refuse deposited in said opening; engine means for driving said vehicle and including a'transmission provided with a plurality of selectable speed ranges and a power takeoff means; fluid. motor means for driving said packer blade; pu'mp means driven by said power take-off means and in circuit with said fluid motor; fluid reservoir means; flow divider control means in said circuit for delivering a predetermined controlled volumetric flow of fluid from the pump to said fluid motor means,

said volumetric flow being independent of increases in the speed of said engine; automatic throttle control means for increasing the speed of said engine above normal idle to provide adequate fluid flow to operate said packer blade; manual transmission control means for said transmission including a neutral position and at least Onefdrive position, said automatic throttle control means being operative with said transmission control means in the neutral position; and means for preventing operation of said automatic throttle control means when said transmission control means in in said drive position.

2. The apparatus defined in claim 1 wherein said automatic throttle control means includes an electric actuator in circuit with a source of electrical energy; and wherein said means for preventing operation of said automatic throttle control means comprises a switch operated by said transmission control means and in circuit with said electric actuator. 

1. A refuse truck comprising, in combination, a refuse receiving body including a load receiving opening; a packer blade moveably mounted on said body and including a compacting surface for engaging refuse deposited in said opening; engine means for driving said vehicle and including a transmission provided with a plurality of selectable speed ranges and a power take-off means; fluid motor means for driving said packer blade; pump means driven by said power take-off means and in circuit with said fluid motor; fluid reservoir means; flow divider control means in said circuit for delivering a predetermined controlled volumetric flow of fluid from the pump to said fluid motor means, said volumetric flow being independent of increases in the speed of said engine; automatic throttle control means for increasing the speed of said engine above normal idle to provide adequate fluid flow to operate said packer blade; manual transmission control means for said transmission including a ''''neutral'''' position and at least one ''''drive'''' position, said automatic throttle control means being operative with said transmission control means in the neutral position; and means for preventing operation of said automatic throttle control means when said transmission control means in in said ''''drive'''' position.
 2. The apparatus defined in claim 1 wherein said automatic throttle control means includes an electric actuator in circuit with a source of electrical energy; and wherein said means for preventing operation of said automatic throttle control means comprises a switch operated by said transmission control means and in circuit with said electric actuator. 